CN1894499A - Valve arrangement in particular inlet valve for a high pressure fuel pump - Google Patents
Valve arrangement in particular inlet valve for a high pressure fuel pump Download PDFInfo
- Publication number
- CN1894499A CN1894499A CNA2004800369928A CN200480036992A CN1894499A CN 1894499 A CN1894499 A CN 1894499A CN A2004800369928 A CNA2004800369928 A CN A2004800369928A CN 200480036992 A CN200480036992 A CN 200480036992A CN 1894499 A CN1894499 A CN 1894499A
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- Prior art keywords
- section
- control valve
- longitudinal axis
- valve unit
- passage
- Prior art date
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- Pending
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- 239000000446 fuel Substances 0.000 title claims abstract description 32
- 239000012530 fluid Substances 0.000 claims abstract description 31
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 5
- 230000007704 transition Effects 0.000 claims description 9
- 238000005452 bending Methods 0.000 claims description 4
- 238000005260 corrosion Methods 0.000 claims description 3
- 230000007797 corrosion Effects 0.000 claims description 3
- 239000006181 electrochemical material Substances 0.000 claims description 3
- 238000000034 method Methods 0.000 claims description 3
- 230000008569 process Effects 0.000 claims description 3
- 238000009825 accumulation Methods 0.000 description 3
- 230000002349 favourable effect Effects 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 238000005299 abrasion Methods 0.000 description 1
- 230000001154 acute effect Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 238000010304 firing Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000002347 injection Methods 0.000 description 1
- 239000007924 injection Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
- F02M59/06—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/462—Delivery valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0452—Distribution members, e.g. valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/001—Noise damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/06—Venting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/206—Flow affected by fluid contact, energy field or coanda effect [e.g., pure fluid device or system]
- Y10T137/2087—Means to cause rotational flow of fluid [e.g., vortex generator]
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
A valve arrangement (47), for a high-pressure fuel pump (16), comprises a valve element (46), arranged in a valve chamber (42) and a fluid channel (30), contiguous with the valve chamber (42) upstream thereof. According to the invention, the fluid channel (30) is embodied such that the fluid flow entering the valve chamber (42) is at least partly forced to undergo a rotation about a longitudinal axis (40) of the fluid channel (30) (swirl).
Description
Prior art
The present invention relates to the inlet valve device of a kind of control valve unit, especially a high pressure fuel pump, this control valve unit has one and is arranged on valve element in the valve pocket and one in upstream and the adjacent fluid passage of this valve pocket.
The control valve unit of the described type of beginning part is disclosed by market.It for example is applied on the high pressure fuel pump of a common-rail injection system.This high pressure fuel pump is configured and survives (post) plug pump.Be provided with a ball check valve as the inlet valve that leads to a conveying chamber.The ball of safety check is set in the valve pocket, and an input hole leads in this valve pocket.Input hole comprises: a first passage section, and this channel section is substantially perpendicular to the longitudinal axis of the piston of reciprocating pump; And a second channel section, the longitudinal axis of the piston of the relative reciprocating pump of this section is arranged coaxially.The longitudinal axis of these two channel section intersects in an intersecting area.The deflection of an acute angle of the fuel of appearance inflow inlet valve in this intersecting area when reciprocating pump is worked.
Task of the present invention is that the control valve unit of splitting the described type of initial portion improves in this wise, so that it is worked and the efficient of (for example) high pressure fuel pump that wherein uses this control valve unit is improved as far as possible losslessly.
This task solves on the control valve unit of the described type of beginning part like this, and promptly the fluid passage is constructed in this wise, the commentaries on classics (vortex) that the longitudinal axis that makes the fluid stream that flows into valve pocket have the hydrodynamic form passage revolves.
Advantage of the present invention
The rotation (" vortex " or " spin ") that adds in flowing causes centrifugal force, and by these centrifugal force, flowing is forced on the wall.Can prevent in this way: for example when direction changes, forming the wall that fluid stream breaks away from the fluid passage under the situation of corresponding negative pressure region.Can avoid stagnation pressure (Staudruck) and flow resistance in turn-around zone to descend thus.And avoided the cavitation erosion in the fluid passage to damage further.Because the fluid that is close on the fluidic channel walls flows, the fluid passage is injected fluid equably, and this can cause bigger throughput under the identical situation of opening the endurance of valve member.
In addition, because any moment is close to flowing of wall, the length of fluid passage can be done forr a short time, and this makes control valve unit and uses the physical dimension of (for example) petrolift of this control valve unit always to reduce therein.By having flowing of vortex, can avoid or prevent fully the flow process (velocity curve of pulse shape) of unborn extremely unsettled turbulent flow, this has reduced the load in a fluid passage and an other zone that is arranged on the upstream.Therefore also be to fluid being imported the saving of the transfer pump of control valve unit.
Flow uniformly by becoming in the fluid passage, valve element itself is also streamed equably and also remained on the center thus under the state of suspension of opening, in other words, by unilaterally aside flowing liquid on valve, do not produce any transverse force.This causes the improvement of control valve unit efficient and reducing of valve component abrasion equally.
Favourable further configuration of the present invention provides in the dependent claims.
At first propose, the fluid passage comprises a first passage section and a second channel section that is connected with this first passage section, wherein the longitudinal axis of channel section is each other in an angle less than 180 °, and reaching wherein, the longitudinal axis of the relative second channel section of longitudinal axis of first passage section laterally misplaces.Cause the rotation of in the second channel section, flowing with plain mode by this side direction dislocation.Thus can be effectively the level and smooth because turbulent flow that the bending between two channel section produces, or can not form this turbulent flow.
When the longitudinal axis of two channel section roughly becomes a right angle at least each other, then should rotate obvious especially.In the case, the mobile vortex that is coupled with in the second channel section is the strongest, and therefore also maximum by the accessible advantage of control valve unit according to the present invention.
The present invention also proposes, and this control valve unit comprises a ball or a conic section, as the valve element.Also make rotational symmetric valve element form rotation owing to flow into the rotatablely moving of fluid of valve pocket.This has prevented the one-sided wearing and tearing on the described valve element and has improved the durability that the valve seat of valve element is given in configuration.
Feature according to a particularly preferred configuration of control valve unit of the present invention is: two channel section have roughly the same at least radius in cross section; And the dislocation of the side direction of these longitudinal axis is greater than this radius.This has simplified according to the manufacturing of control valve unit of the present invention and has reduced manufacture cost thus, because can use identical drilling tool for two channel section.
The present invention also proposes, and the transition region between first passage section and the second channel section is processed by electrochemical material corrosion.This can realize the transition of first passage section to the no seamed edge to a great extent of another channel section, and this also is favourable for flowing uniformly.
Particularly preferably be in the case, comprise crooked wall to the transition region of second channel section from the first passage section.This causes level and smooth especially flowing, and occurs turbulent flow seldom in this flows.
Particularly preferably be, the first passage section extends not more than on axially or does not surpass the second channel zone at all.Reduced thus from the stagnation pressure of first passage section to the upstream of second channel section deflection, this further reduces flow resistance and always is improved in the hydraulically operated efficient of control valve unit that makes.
Can also be that the longitudinal axis of the longitudinal axis of first passage section and second channel section folds one greater than 90 ° angle.This has caused additional resistance to descend.
Description of drawings
Describe a particularly preferred embodiment of the present invention in detail hereinafter with reference to accompanying drawing.Accompanying drawing is represented:
Fig. 1: summary view with internal-combustion engine of a high pressure fuel pump;
Fig. 2 a: cross section of the housing of Fig. 1 mesohigh petrolift;
Fig. 3: along the cross section of the line III-III of Fig. 2;
Fig. 4: a details IV among Fig. 2;
Fig. 5: along the cross section of the line V-V of Fig. 4;
Fig. 6: along the cross section of the line VI-VI of Fig. 4;
Fig. 7: along the cross section of the line VII-VII of Fig. 6;
The view form of implementation of a modification of the housing of the high pressure fuel pump of Fig. 8: Fig. 1, that be similar to Fig. 3.
Embodiment
An internal-combustion engine always has a reference number 10 in Fig. 1.It comprises that 12, one prime transfer pumps 14 of a fuel container are transported to a high pressure fuel pump 16 by this fuel container with fuel.This high pressure fuel pump is reduced to a very high pressure with fuel pressure and is transported to a fuel accumulation pipe 18 (" Rail "-" rail "), and fuel under high pressure is stored in this fuel accumulation pipe.Connected a plurality of spargers 20 on fuel accumulation pipe, they directly are ejected into fuel in their pairing firing chambers 22.
In Fig. 2 and 3, express the housing 24 of this high pressure fuel pump 16 in further detail.This housing comprises three cylinder 26a, 26b and 26c, and they constitute substantially the samely.For simplicity, below only with reference to cylinder 26a.
In cylinder 26a, have a piston hole 28, vertically received a unshowned piston therein movably.Piston hole 28 can be connected with a fuel inlet 32 by a fluid passage 30.Fuel inlet 32 is connected with prime transfer pump 14 again.
As especially appreciable from Fig. 6, has one in the transition region between first passage section 34 and second channel section 36 from the wall 41 of first passage section 34 to 36 bendings of second channel section.This wall processes by electrochemical material corrosion.The wall of radially outer in the sectional plane of Fig. 6 of channel section 34 does not carry out the transition to the respective wall section of channel section 36 with having bending or seamed edge by this wall 41.
Between the second channel section 36 of fluid passage 30 and piston hole 28, be provided with a valve pocket 42.Be configured with a stage between valve pocket 42 and second channel section 36, this stage is configured for a valve seat 44 of valve ball 46, and this valve ball is received in (referring to Fig. 4 and 5) in the valve pocket 42.Valve ball 46 is loaded on valve seat 44 by a unshowned in the drawings spring.Be connected a conveying chamber 47 with valve pocket 42.As especially appreciable by Fig. 7, first passage section 34 extends beyond second channel section 36 hardly.Fluid passage 30, valve seat 44 and valve ball 46 always constitute a control valve unit 47.
High pressure fuel pump 16 will work as follows (here also being) with reference to cylinder 26a:
Valve ball 46 lifts from valve seat 44 when the intake stroke of piston.Fuel now from prime transfer pump 14 by fuel inlet 32, first passage section 34, second channel section 36 and pass valve ball 46 and valve seat 44 between Clearance Flow to the valve pocket 42 and again in conveying chamber 47.Because the dislocation V between the longitudinal axis 38 of first passage section 34 and the longitudinal axis 40 of second channel section 36, fluid stream is subjected to a lateral movement component (arrow 48 among Fig. 6).This lateral movement component is subjected to the support of crooked wall 41, and can not set up a tangible stagnation pressure thus in first passage section 34.
Fuel arrives second channel section 36 from first passage section 34.Fuel is subjected to 90 ° direction change in the case.But because lateral movement component 48, rotatablely moving around the longitudinal axis 40 of second channel section 36 will appear additionally when fluid flows in the second channel section 36.This rotatablely moves and is also referred to as " vortex " or " spin " and is provided with label 50 in Fig. 6 and 7.When changing direction in the transition region of fluid stream between first passage section 34 and second channel section 36, can stop mobile separation by vortex 50, this flow separation will cause the dangerous of the increase of flow resistance and the formation of cavitating and cause corresponding wearing and tearing.
Also make the valve ball 46 in open mode form rotation by vortex 50, it is worn and torn equably.Therefore can on the very long time, keep its sealing function and the sealing function of valve seat 44.Because prevented in the transition region between two channel section 34 and 36 and fuel in second channel section 36 separating of flowing especially, can not cause that also fluid stream shrinks with corresponding waterpower of dwindling (hydraulisch) diameter, this hydraulic diameter that dwindles will cause the enhancing of throttling.
Express the form of implementation of a modification among Fig. 8.Here has identical label with the parts of top accompanying drawing and those parts and the zone of regional identical functions.They are no longer explained.With first embodiment differently, the longitudinal axis 40 of the longitudinal axis 38 relative second channel sections 36 of first passage section 34 is not into 90 ° angle but becomes about 45 ° angle here.Can additionally realize thus one more favourable, be littler the flowing of resistance.
Claims (9)
1. control valve unit (47), especially the inlet valve device of a high pressure fuel pump (16), this control valve unit has the valve element (46) and the fluid passage (30) in upstream and this valve pocket (42) adjacency that are arranged in the valve pocket (42), it is characterized in that: this fluid passage (30) are constituted in this wise, make the fluid stream that flows into valve pocket (42) have the rotation (vortex) of the longitudinal axis (38,40) of hydrodynamic form passage (30).
2. according to the control valve unit (47) of claim 1, it is characterized in that: this fluid passage comprises a first passage section (34) and a second channel section (36) that is connected with this first passage section, these channel section (34 wherein, 36) longitudinal axis (38,40) each other in a angle less than 180 °, and the relative longitudinal axis (40) of second channel section (36) laterally misplace (V) of longitudinal axis (38) of first passage section (34) wherein.
3. according to the control valve unit (47) of claim 2, it is characterized in that: the longitudinal axis (38,40) of these two channel section (34,36) roughly becomes a right angle at least each other.
4. according to one control valve unit (47) in the above claim, it is characterized in that: this control valve unit comprises that a ball (46) or a conic section are as the valve element.
5. according to one control valve unit (47) in the claim 2 to 4, it is characterized in that: two channel section (34,36) have roughly the same radius in cross section; The side direction dislocation (V) of these longitudinal axis (38,40) is greater than this radius.
6. according to one control valve unit (47) in the claim 2 to 5, it is characterized in that: the transition region between first passage section (34) and the second channel section (36) by electrochemical material corrosion process.
7. according to the control valve unit (47) of claim 6, it is characterized in that: described transition region comprises one from the wall (41) of first passage section (34) to second channel section (36) bending.
8. according to one control valve unit (47) in the claim 2 to 7, it is characterized in that: first passage section (34) is no more than or does not surpass the second channel zone at all on axially and extends (36).
9. according to one control valve unit (47) in the above claim, it is characterized in that: the longitudinal axis of the longitudinal axis of first passage section (34) and second channel section (36) folds one greater than 90 ° angle.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10357612.6 | 2003-12-10 | ||
| DE2003157612 DE10357612A1 (en) | 2003-12-10 | 2003-12-10 | Valve arrangement, in particular inlet valve of a high-pressure fuel pump |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1894499A true CN1894499A (en) | 2007-01-10 |
Family
ID=34638560
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2004800369928A Pending CN1894499A (en) | 2003-12-10 | 2004-10-21 | Valve arrangement in particular inlet valve for a high pressure fuel pump |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20080190502A1 (en) |
| EP (1) | EP1700028B1 (en) |
| JP (1) | JP4373447B2 (en) |
| CN (1) | CN1894499A (en) |
| DE (2) | DE10357612A1 (en) |
| WO (1) | WO2005057004A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109964032A (en) * | 2016-10-20 | 2019-07-02 | 罗伯特·博世有限公司 | High-pressure pump for fuel injection system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ITMI20080288A1 (en) * | 2008-02-22 | 2009-08-23 | Bosch Gmbh Robert | HIGH PRESSURE PUMP FOR HIGH PRESSURE FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE |
| DE102009000945A1 (en) * | 2009-02-18 | 2010-08-19 | Robert Bosch Gmbh | fuel pump |
| JP6988196B2 (en) * | 2017-06-27 | 2022-01-05 | 株式会社Soken | Fuel injection device |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US712929A (en) * | 1901-10-28 | 1902-11-04 | George M Hendee | Valve for internal-combustion engines. |
| US1105134A (en) * | 1913-11-12 | 1914-07-28 | Engelbert Hanemann | Carbureter. |
| US1517598A (en) * | 1921-09-01 | 1924-12-02 | Stevenson John William | Apparatus for spraying fluids and mixing the same |
| US3220517A (en) * | 1962-10-30 | 1965-11-30 | Best available copy | |
| US3797510A (en) * | 1971-10-28 | 1974-03-19 | Purolator Inc | Crashworthy valve |
| US3854468A (en) * | 1972-01-17 | 1974-12-17 | Rheem Mfg Co | Vortex humidifier for forced flow hot air furnace |
| US3921656A (en) * | 1974-06-20 | 1975-11-25 | Spectrum Ass Inc | Self-closing breakaway valve assemblies |
| US4131134A (en) * | 1977-05-04 | 1978-12-26 | Owen, Wickersham & Erickson | Fluid flow regulator |
| US4157281A (en) * | 1977-07-14 | 1979-06-05 | Systems Technology Corp | Method and apparatus for reclaiming solvents from solvent-bearing sludge material |
| US4574451A (en) * | 1982-12-22 | 1986-03-11 | General Electric Company | Method for producing an article with a fluid passage |
| US4827961A (en) * | 1987-10-13 | 1989-05-09 | Helix Enterprises, Inc. | High velocity fluid swivel joint coupling |
| DE3804843A1 (en) * | 1988-02-17 | 1989-08-31 | Bosch Gmbh Robert | FUEL INJECTION PUMP FOR INTERNAL COMBUSTION ENGINES |
| DE3843819A1 (en) * | 1988-09-09 | 1990-03-22 | Bosch Gmbh Robert | PRESSURE VALVE |
| DE3937707A1 (en) * | 1988-12-24 | 1991-05-16 | Bosch Gmbh Robert | Pressure valve for engine fuel line - has control collar with helical recess formed in valve closure |
| DE19500690B4 (en) * | 1995-01-12 | 2004-05-19 | Robert Bosch Gmbh | Fuel supply system and method for operating a fuel supply system |
| DE19541507A1 (en) * | 1995-11-08 | 1997-05-15 | Bosch Gmbh Robert | Fuel injection device for internal combustion engines |
| JP2001246216A (en) * | 1999-12-28 | 2001-09-11 | Denso Corp | Gas-liquid separator |
| US6659118B2 (en) * | 2001-12-04 | 2003-12-09 | Ecotechnology, Ltd. | Flow development chamber |
| US7082955B2 (en) * | 2001-12-04 | 2006-08-01 | Ecotechnology, Ltd. | Axial input flow development chamber |
| DE502004007338D1 (en) * | 2003-05-22 | 2008-07-17 | Bosch Gmbh Robert | Check valve, in particular for a high-pressure pump of a fuel injection device for an internal combustion engine |
| JP4260697B2 (en) * | 2004-06-29 | 2009-04-30 | 三菱電機株式会社 | solenoid valve |
-
2003
- 2003-12-10 DE DE2003157612 patent/DE10357612A1/en not_active Withdrawn
-
2004
- 2004-10-21 EP EP04802632A patent/EP1700028B1/en active Active
- 2004-10-21 CN CNA2004800369928A patent/CN1894499A/en active Pending
- 2004-10-21 US US10/581,415 patent/US20080190502A1/en not_active Abandoned
- 2004-10-21 JP JP2006543352A patent/JP4373447B2/en not_active Expired - Fee Related
- 2004-10-21 WO PCT/DE2004/002343 patent/WO2005057004A1/en active IP Right Grant
- 2004-10-21 DE DE200450006447 patent/DE502004006447D1/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109964032A (en) * | 2016-10-20 | 2019-07-02 | 罗伯特·博世有限公司 | High-pressure pump for fuel injection system |
| CN109964032B (en) * | 2016-10-20 | 2021-10-01 | 罗伯特·博世有限公司 | High-pressure pump for a fuel injection system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2007513292A (en) | 2007-05-24 |
| EP1700028B1 (en) | 2008-03-05 |
| WO2005057004A1 (en) | 2005-06-23 |
| US20080190502A1 (en) | 2008-08-14 |
| DE502004006447D1 (en) | 2008-04-17 |
| EP1700028A1 (en) | 2006-09-13 |
| JP4373447B2 (en) | 2009-11-25 |
| DE10357612A1 (en) | 2005-07-07 |
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Legal Events
| Date | Code | Title | Description |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| AD01 | Patent right deemed abandoned |
Effective date of abandoning: 20070110 |
|
| C20 | Patent right or utility model deemed to be abandoned or is abandoned |